CN113987863A - Acoustic transmission performance simulation calculation method based on dome structure design scheme - Google Patents

Acoustic transmission performance simulation calculation method based on dome structure design scheme Download PDF

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CN113987863A
CN113987863A CN202111202237.4A CN202111202237A CN113987863A CN 113987863 A CN113987863 A CN 113987863A CN 202111202237 A CN202111202237 A CN 202111202237A CN 113987863 A CN113987863 A CN 113987863A
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邹欢
苏帅
徐峰
周伟
陈鑫
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Abstract

The invention provides an acoustic transmission performance simulation calculation method based on a dome structure design scheme, which adopts a fluid-solid coupling finite element technology, mainly analyzes the aspects of model simplification and establishment, grid division, boundary condition setting calculation and the like, verifies the accuracy of numerical simulation by calculating the insertion loss of a finite element model of a dome acoustic transmission window without reinforcing ribs and comparing a numerical simulation result with a theoretical analysis result.

Description

Acoustic transmission performance simulation calculation method based on dome structure design scheme
Technical Field
The invention belongs to the technical field of general acoustic design of sonar air guide hoods of surface ships, and particularly relates to an acoustic transmission performance simulation calculation method based on an air guide hood structure design scheme.
Background
The guide cover is a sound-transmitting shell which ensures that the sonar is in a good working environment in water. In addition to the requirement of low flow noise, the design of the air guide sleeve also needs to have both mechanical properties and static acoustic properties, i.e. sufficient strength and good sound permeability.
In recent years, pod design based on sonar acoustic characteristics has been gradually discussed abroad from a system theory perspective, and various simulation methods have been developed to simulate the self-noise of a sonar platform area. The acoustic design of the sonar air guide sleeve often conflicts with the structural design, a proper design can be found out from various contradictory requirements through a numerical simulation tool, and the importance of a numerical simulation technology in the acoustic design of the sonar air guide sleeve is explained by taking the example that sound waves are incident into a theoretical model and a finite element model of the air guide sleeve insertion loss for comparison.
The surface ship in China lacks systematic and fine work in the aspects of the structure form, the sound transmission performance, the acoustic material treatment and the like of the air guide sleeve, and particularly the acoustic environment in the sleeve is hardly detected and researched. At present, the field of auxiliary air guide sleeve acoustic design by utilizing a numerical simulation technology in China is blank, and gradual exploration is also needed for judging whether a calculation result is reliable and whether the accuracy requirement required by engineering development can be met. The method can improve the overall acoustic design level of the inventor by developing the numerical simulation technical research of the sound transmission performance of the sound transmission window of the air guide sleeve in related model scientific research work.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a sound transmission performance simulation calculation method based on a design scheme of a dome structure aiming at the existing problems.
The technical scheme adopted by the invention for solving the technical problems is as follows: a sound transmission performance simulation calculation method based on a design scheme of a flow guide cover structure is characterized by comprising the following steps:
s1) modeling: according to the size of the simplified model, a double-layer plate model is established by using an SOLID5 unit, water filling environments are established at two ends and inside of the double-layer plate model by using a FLUID30 unit, a coupling layer is established at the contact surface of the double-layer plate model and a water medium, plane wave sound pressure assignment is carried out at the leftmost end of a water layer, and a full sound absorption is established by using a FLUID130 unit at the rightmost end of the water layer to simulate an infinite environment;
s2) dividing the grid: calculating the wavelength lambda of the minimum stress waveminThen analyzing the vibration wave wavelength lambda corresponding to the upper limit of the frequencyBDetermining the standard of finite element meshing of the sound-transmitting window model of the air guide sleeve;
s3) solving calculation: after modeling and grid division are finished, selecting a calculated step length according to a calculated frequency band, and performing solution calculation;
s4) data post-processing: according to the calculation method of the insertion loss in the standing wave field, selecting incident sound pressure P at proper positions at two ends of the double-layer plate modeliReflected sound pressure PrTransmission sound pressure PtAnd calculating insertion loss, and imaging the result by using software MATLAB after obtaining the result of the insertion loss.
According to the above scheme, step S2 specifically includes the following contents:
starting from wave theory, at least five nodes, i.e. four elements, should be present in a wavelength, from which a refinement of the element length, i.e. the element length, is derived
Figure BDA0003305396010000021
Refinement criteria derived from the fluctuation theory are as follows:
the longitudinal wavelength wave velocity in the plate is:
Figure BDA0003305396010000022
the bending wave velocity in the plate is:
Figure BDA0003305396010000023
wavelength of vibration wave corresponding to upper limit of frequency:
Figure BDA0003305396010000031
wherein h is the plate thickness, E is the elastic modulus, mu is the Poisson's ratio, and rho is the density; substituting the upper limit value of the frequency to calculate and obtain the wavelength lambda of the vibration wave corresponding to the upper limit value of the frequencyBI.e. the minimum stress wavelength value at the upper limit of frequency, and then the cell size delta is obtained.
According to the above scheme, step S4 specifically includes the following contents:
the measured sample is placed in the center of a standing wave field, the front of the sample is an incident part of sound waves, the rear of the sample is a transmission part, the incident part forms the standing wave field due to the reflection of the surface of the sample, the incident waves and the reflected waves are separated by adopting a standing wave separation method, only transmission waves are theoretically required to exist in the transmission part, therefore, the tail end of a sound absorption wedge is arranged to ensure that the transmission part is a traveling wave field in a test frequency band, when the condition of a plane wave sound field is met in a tube and the attenuation of water media in the field is neglected, the sound pressure at the position of a distance x in front of the sample can be written as:
Figure BDA0003305396010000032
the above formula shows that the sound field in the tube is a superposition of two plane waves, wherein
Figure BDA0003305396010000033
Then the transformation can be:
Figure BDA0003305396010000034
wherein k is the wave number;
the norm of p (x) is:
Figure BDA0003305396010000035
the above formula shows that
Figure BDA0003305396010000036
When, | p (x) | shows a maximum value; when in use
Figure BDA0003305396010000037
When | p (x) | exhibits a minimum value; order: (vi) sweet food SWR ═ p (x)max/|p(x)|minWhere SWR is standing wave ratio, SWR ═ 1+ R)/(1-R), and the magnitude of the reflection coefficient is: r ═ (SWR-1)/(SWR + 1);
transmission coefficient: t ═ pt/pi＝pt(1-R)/|p(x)|min＝pt(1+R)/|p(x)|max；
The insertion loss is: t isp＝-20lgT。
The invention has the beneficial effects that: the method adopts a fluid-solid coupled finite element technology, mainly analyzes the aspects of model simplification and establishment, grid division, boundary condition setting calculation and the like, verifies the accuracy of numerical simulation by calculating the insertion loss of a finite element model of the sound-transmitting window of the guide cover without reinforcing ribs and comparing the numerical simulation result with a theoretical analysis result, carries out numerical simulation on the insertion loss of the sound-transmitting window of the guide cover with the reinforcing ribs, and can be used for guiding engineering development.
Drawings
FIG. 1 is a schematic diagram of a standing wave tube method for measuring insertion loss according to an embodiment of the present invention.
Fig. 2 is a layout view of a pod configuration according to an embodiment of the present invention.
Fig. 3 is a diagram of an acoustic window model (without ribs) according to one embodiment of the present invention.
Fig. 4 is a diagram of an acoustic window model (with reinforcing ribs) according to an embodiment of the present invention.
Fig. 5 is a sound pressure distribution of a plane wave perpendicularly incident through two metal plates according to an embodiment of the present invention.
FIG. 6 is a graph comparing analytical values with an insertion loss finite element solution according to an embodiment of the present invention.
FIG. 7 is a grid partitioning diagram of a computing area, according to one embodiment of the present invention.
FIG. 8 is a graph of insertion loss for a two-layer plate model according to one embodiment of the present invention.
Detailed Description
For a better understanding of the present invention, reference is made to the following description taken in conjunction with the accompanying drawings and examples.
A sound transmission performance simulation calculation method based on a design scheme of a flow guide cover structure comprises the following steps:
s1) modeling: according to the size of the simplified model, a double-layer plate model is established by using an SOLID5 unit, water filling environments are established at two ends and inside of the double-layer plate model by using a FLUID30 unit, a coupling layer is established at the contact surface of the double-layer plate model and a water medium, plane wave sound pressure assignment is carried out at the leftmost end of a water layer, and a full sound absorption is established by using a FLUID130 unit at the rightmost end of the water layer to simulate an infinite environment;
s2) dividing the grid: calculating the wavelength lambda of the minimum stress waveminThen analyzing the vibration wave wavelength lambda corresponding to the upper limit of the frequencyBDetermining the standard of finite element meshing of the sound-transmitting window model of the air guide sleeve;
s3) solving calculation: after modeling and grid division are finished, selecting a calculated step length according to a calculated frequency band, and performing solution calculation;
s4) data post-processing: according to the calculation method of the insertion loss in the standing wave field, selecting incident sound pressure P at proper positions at two ends of the double-layer plate modeliReflected sound pressure PrTransmission sound pressure PtAnd calculating insertion loss, and imaging the result by using software MATLAB after obtaining the result of the insertion loss.
Starting from wave theory, at least five nodes, i.e. four elements, should be present in a wavelength, from which a refinement of the element length, i.e. the element length, is derived
Figure BDA0003305396010000051
Refinement criteria derived from the fluctuation theory are as follows:
the longitudinal wavelength wave velocity in the plate is:
Figure BDA0003305396010000052
the bending wave velocity in the plate is:
Figure BDA0003305396010000053
wavelength of vibration wave corresponding to upper limit of frequency:
Figure BDA0003305396010000054
wherein h is the plate thickness, E is the elastic modulus, mu is the Poisson's ratio, and rho is the density; substituting the upper limit value of the frequency to calculate and obtain the wavelength lambda of the vibration wave corresponding to the upper limit value of the frequencyBI.e. the minimum stress wavelength value at the upper limit of frequency, and then the cell size delta is obtained.
The thickness h is 4mm, and the elastic modulus E is 1.16 × E11Pa, poisson ratio μ 0.32, density ρ 4500kg/m3For example, λ is when the upper frequency limit is 15kHzB0.0446, the cell size should be less than 0.01115 m.
As shown in FIG. 1, the sample to be measured is placed in the center of the standing wave field, the front of the sample is an incident part of sound waves, and the rear of the sample is a transmission part. Because of the reflection on the surface of the sample, the incident part forms a standing wave field, and a standing wave separation method is necessary to separate the incident wave from the reflected wave. In the transmission part, only transmission waves are theoretically required to exist, so that the tail end of the acoustic wedge is arranged to ensure that the transmission part is a traveling wave field in the test frequency band.
When the plane wave acoustic field conditions are met in the tube and the attenuation of the aqueous medium in the field is negligible, the sound pressure at distance x in front of the sample can be written as:
Figure BDA0003305396010000061
the above formula shows that the sound field in the tube is a superposition of two plane waves, wherein
Figure BDA0003305396010000062
Then the transformation can be:
Figure BDA0003305396010000063
wherein k is the wave number;
the norm of p (x) is:
Figure BDA0003305396010000064
the above formula shows that
Figure BDA0003305396010000065
When, | p (x) | shows a maximum value; when in use
Figure BDA0003305396010000066
When | p (x) | exhibits a minimum value; order: (vi) sweet food SWR ═ p (x)max/|p(x)|minWhere SWR is standing wave ratio, SWR ═ 1+ R)/(1-R), and the magnitude of the reflection coefficient is: r ═ (SWR-1)/(SWR + 1);
transmission coefficient: t ═ pt/pi＝pt(1-R)/|p(x)|min＝pt(1+R)/|p(x)|max；
The insertion loss is: t isp＝-20lgT。
Example one
Based on the design scheme of the fairwater structure of the surface ship, as shown in figure 2, the sound-transmitting window of the fairwater adopts a double-layer plate shell structure, and the thickness of each layer of plate is 4 mm. Reinforcing ribs are horizontally and radially arranged between the double-layer plates, the distance between the horizontal reinforcing ribs is 400mm, and the distance between the radial reinforcing ribs is 500 mm. The horizontal and radial reinforcing ribs are rectangular reinforcing structures with the width multiplied by 25 mm.
In order to avoid the situation that the number of the divided units is too large, the requirements on the configuration of computer hardware and the calculation time are high, the sound transmission window structure needs to be simplified. Considering the reasons of calculation amount, the 4 double-layer plate window panes with the size of 1000mm × 800mm at the center of the sound-transmitting window are selected, the simplified sound-transmitting window model (without reinforcing ribs) is shown in fig. 3, and if the cross-shaped reinforcing ribs are reserved, the simplified sound-transmitting window model (with reinforcing ribs) is shown in fig. 4.
Water layers are built at two ends and inside of the double-layer plate model without the reinforcing ribs by using the FLUID30 unit, the total length of the water layers is 2m, planar wave sound pressure assignment is carried out at the leftmost end (x is-1.0 m) of the water layers, and full sound absorption is built at the rightmost end (x is-1.0 m) of the water layers by using the FLUID130 unit to simulate an infinite environment. And dividing the double-layer plate and the surrounding water layers into grids, and performing simulation calculation on the insertion loss of the simplified model by adopting the intellectual achievement.
And (3) calculating the theoretical analytical value of the insertion loss of the double-layer plate with the sound wave vertical incidence spacing of 25mm, which comprises the following steps:
when the plane wave is incident on the plane interface of the two media, part of the sound energy is reflected to form a reflected wave; part of the sound energy penetrates through the interface and enters another medium to form a refracted wave.
It is assumed that the mid-water plane acoustic wave is incident perpendicularly to an infinite, uniform, parallel two-layer metal plate, as shown in fig. 5. The thickness of the plate is l and the distance between the plates is d. The general solution form of the sound pressure wave equation in each water area is as follows:
p1i＝PA1ie-jkx
p1r＝PA1re-jkx
p3t＝PA3te-jk(x-l)
p3r＝PA3rejk(x-l)
p5t＝PA5te-jk(x-d-2l)
wherein p is1iPlane wave sound pressure, p, of normal incidence1r、p3rIs the sound pressure of the reflected wave, p3t、p5tIs a transmitted wave sound pressure. Because the left and right sound pressures of the plate are not equal, the plate generates an acceleration
Figure BDA0003305396010000071
. For the left plate, the sound pressure at x 0 and x l is P1＝PA1i+PA1r，P3＝PA3t+PA3r. The equation of motion for the plate is then:
Figure BDA0003305396010000072
since the plate is very thin, i.e., l < lambda, it is known from the particle normal vibration velocity continuous condition: the particle velocities at x-0 and x-l can all be considered to be equal to the plate velocity, i.e.:
Figure BDA0003305396010000073
from the above formula, one can obtain: j ω M (P)A1i-PA1r)/z1＝jωM(PA3t-PA3r)/z1＝P1-P3；
The same applies to the right plate where x ═ d + l and x ═ d +2 l:
jωM(PA3te-jkd-PA3rejkd)/z1＝jωMPA5t/z1＝PA3te-jkd+PA3rejkd-PA5t；
from the above formula, one can obtain:
Figure BDA0003305396010000081
where M is the mass of the sheet per unit area, where M is ρ l, where ρ is the density of the material; z1 is the characteristic impedance of water.
The insertion loss of the double-layer metal plate is:
Figure BDA0003305396010000082
the analysis value is compared with the insertion loss finite element solution of the double-layer plate model without the reinforcing ribs for analysis, as shown in figure 6, the calculation results of the finite element algorithm and the analysis method are well matched within the error allowable range, and the feasibility of the intellectual achievement is fully verified.
After the feasibility of the FLUID-solid coupling finite element algorithm is verified, water layers are built at two ends and inside a double-layer plate model with reinforcing ribs reserved by using the FLUID30 unit, the total length of the water layers is 0.8m in consideration of the reasons of calculated amount, plane wave sound pressure assignment is carried out at the leftmost end (x is-0.4 m) of the water layers, and full sound absorption is built at the rightmost end (x is-0.4 m) of the water layers by using the FLUID130 unit to simulate an infinite environment. The model and surrounding water layer are gridded as shown in figure 7. By adopting the intellectual achievement, the insertion loss of the simplified model is subjected to simulation calculation, and the simulation calculation result is shown in fig. 8.
It can be seen from fig. 8 that, in the frequency band of 10kHz to 15kHz, the insertion loss values of most frequency points are within 1.5dB, and the insertion loss values of some frequency points (12.2kHz, 13.6kHz, 13.7kHz, and 14.1kHz) are higher than 2dB, because the acoustic window finite element model coupled with the aqueous medium resonates under the condition that the sound wave is vertically incident, and the frequency points are resonant frequency points. The resonance frequency point is the inherent characteristic of the whole system, and once the size and the distance of the sound-transmitting window, the size of the reinforcing rib and the amplitude or the phase of the incident sound wave are changed, the resonance frequency point can be changed accordingly.
In order to more intuitively understand the variation trend of the numerical simulation result (discrete value), the calculation result may be subjected to linear fitting, as shown in fig. 8, it can be seen that the fitted insertion loss curve tends to increase in the simulation frequency band.
The above description is only for the preferred embodiment of the intellectual development, but the intellectual development should not be limited to the disclosure of the embodiment and the drawings. All equivalents and modifications which come within the spirit of the disclosure are desired to be protected.

Claims (3)

1. A sound transmission performance simulation calculation method based on a design scheme of a flow guide cover structure is characterized by comprising the following steps:
s1) modeling: according to the size of the simplified model, a double-layer plate model is established by using an SOLID5 unit, water filling environments are established at two ends and inside of the double-layer plate model by using a FLUID30 unit, a coupling layer is established at the contact surface of the double-layer plate model and a water medium, plane wave sound pressure assignment is carried out at the leftmost end of a water layer, and a full sound absorption is established by using a FLUID130 unit at the rightmost end of the water layer to simulate an infinite environment;
s2) dividing the grid: calculating the wavelength lambda of the minimum stress waveminThen analyzing the vibration wave wavelength lambda corresponding to the upper limit of the frequencyBDetermining the standard of finite element meshing of the sound-transmitting window model of the air guide sleeve;
s3) solving calculation: after modeling and grid division are finished, selecting a calculated step length according to a calculated frequency band, and performing solution calculation;
s4) data post-processing: according to the calculation method of the insertion loss in the standing wave field, selecting incident sound pressure P at proper positions at two ends of the double-layer plate modeliReflected sound pressure PrTransmission sound pressure PtAnd calculating insertion loss, and imaging the result by using software MATLAB after obtaining the result of the insertion loss.
2. The method for calculating the sound transmission performance simulation based on the design scheme of the air guide sleeve structure as claimed in claim 1, wherein the step S2 specifically includes the following steps:
starting from wave theory, at least five nodes, i.e. four elements, should be present in a wavelength, from which a refinement of the element length, i.e. the element length, is derived
Figure FDA0003305396000000011
Refinement criteria derived from the fluctuation theory are as follows:
the longitudinal wavelength wave velocity in the plate is:
Figure FDA0003305396000000012
the bending wave velocity in the plate is:
Figure FDA0003305396000000013
wavelength of vibration wave corresponding to upper limit of frequency:
Figure FDA0003305396000000021
wherein the content of the first and second substances,h is plate thickness, E is elastic modulus, mu is Poisson's ratio, and rho is density; substituting the upper limit value of the frequency to calculate and obtain the wavelength lambda of the vibration wave corresponding to the upper limit value of the frequencyBI.e. the minimum stress wavelength value at the upper limit of frequency, and then the cell size delta is obtained.
3. The method for calculating the sound transmission performance simulation based on the design scheme of the air guide sleeve structure as claimed in claim 2, wherein the step S4 specifically includes the following steps:
the measured sample is placed in the center of a standing wave field, the front of the sample is an incident part of sound waves, the rear of the sample is a transmission part, the incident part forms the standing wave field due to the reflection of the surface of the sample, the incident waves and the reflected waves are separated by adopting a standing wave separation method, only transmission waves are theoretically required to exist in the transmission part, therefore, the tail end of a sound absorption wedge is arranged to ensure that the transmission part is a traveling wave field in a test frequency band, when the condition of a plane wave sound field is met in a tube and the attenuation of water media in the field is neglected, the sound pressure at the position of a distance x in front of the sample can be written as:
Figure FDA0003305396000000022
the above formula shows that the sound field in the tube is a superposition of two plane waves, wherein
Figure FDA0003305396000000023
Then the transformation can be:
Figure FDA0003305396000000024
wherein k is the wave number;
the norm of p (x) is:
Figure FDA0003305396000000025
the above formula shows that
Figure FDA0003305396000000026
When, | p (x) | shows a maximum value; when in use
Figure FDA0003305396000000027
When | p (x) | exhibits a minimum value; order: (vi) sweet food SWR ═ p (x)max/|p(x)|minWhere SWR is standing wave ratio, SWR ═ 1+ R)/(1-R), and the magnitude of the reflection coefficient is: r ═ (SWR-1)/(SWR + 1);
transmission coefficient: t ═ pt/pi＝pt(1-R)/|p(x)|min＝pt(1+R)/|p(x)|max；
The insertion loss is: t isp＝-20lgT。
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